Rotary fluid unit



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ROTARY FLUID UNIT Filed Feb. 11, 1965 4 SheetsSheet 1 //VVE/V7'0/?. Lawrence G.Brown ATTORNEY.

Sept. 5, 1967 L. G. BROWN ROTARY FLUID UNIT Filed Feb. 11, 1965 4 Sheets-Sheet 2 FIG.7

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INVENTOR. Lawrence G. Brown y fix? ATTORNEY.

p 5, 1967 L. 6. BROWN 3,339,492

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ROTARY FLUID UNIT Filed Feb. 11, 1965 4 sheetsfigheet 4 IA/I/ l/I/ Ill/[11f] III III I I I 1 1117 III III FIG.|5

INVENTOR. Lawrence G. Brown b'hdk ATTORNEY United States Patent 3,339,492 ROTARY FLUID UNIT Lawrence G. Brown, Montreux-Territet, Switzerland (120 Canyon Acres Drive, Santa Barbara, Calif. 93105) Filed Feb. 11, 1965, Ser. No. 431,874 Claims. (Cl. 103-120) This invention relates to an improvement in rotary fluid units.

It is an object of the present invention to provide a rotary fluid unit having an annular chamber for simplicity of operation and improved performance.

It is another object of the present invention to provide a rotary fluid unit having an annular chamber with rotatable and retractable elements therein for use as a motor or a pump or a brake.

It is a further object of the present invention to provide a plurality of concentric annular chambers in a rotary fluid unit for selection of a variable power output system.

It is yet another object of the present invention to provide a rotary fluid unit having an annular chamber variable in volumetric dimension to provide an infinitely variable torque transmission system.

It is a further object of the present invention to provide a rotary fluid unit having a speed responsive connection and an annular chamber variable in volumetric dimension to provide an infinitely variable torque transmission systern.

In order to fully understand the invention it will be described with respect to the acompanying drawings in which:

FIG. 1 is a cross-section view of the rotary fluid unit of the present invention in an internal combustion engine embodiment;

FIG. 2 is a cross-sectional view of the rotary fluid unit of the present invention in a pump embodiment;

FIG. 3 is a cross-sectional view along line 33 of FIG. 2;

FIG. 4 is a cross-sectional view of the rotary fluid unit of the present invention in a motor or drive embodiment;

FIG. 5 is a cross-sectional view of the rotary fluid unit of the present invention in a brake embodiment;

FIG. 6 is a cross-sectional view of the rotary fluid unit in part showing a ramp element adjacent the wall means;

FIG. 7 is a cross-sectional view taken along line 77 of FIG. 6;

FIG. 8 is a cross-sectional view taken along line 88 of FIG. 6;

FIG. 9 is a plan view of the rotary fluid unit of the present invention embodied in the use of a plurality of annular cylinders;

FIG. 10 is a cross-sectional view taken along line 1010 of FIG. 9;

FIG. 11 is a cross-sectional view showing a device to vary the size of the annular cylinder of the rotary fluid unit of the present invention;

FIG. 12 is a cross-sectional view showing another embodiment to vary the size of the annular cylinder of the rotary fluid unit of the present invention;

FIG. 13 is a cross-sectional view showing a further embodiment to vary the size of the annular cylinder of the rotary fluid unit of the present invention;

FIG. 14 is a cross-sectional view of part of FIG. 13

showing a bypass ararngement; and

FIG. 15 is a view partly in cross-section showing a speed responsive system operable with the fluid units to provide an infinitely variable torque transmission system. With reference to FIG. 1 a rotary fluid unit of the present invention includes a stationary housing 22 and a rotor 24. Attached to rotor 24 are two sets of piston means designated 26a, 26b and 28a, 28b, respectively. In FIG. 1 the rotary fluid unit is embodied as an internal combustion unit. Although the pistons 26a, 26b, 28a and 28b are shown in two sets, it is understood that more than two sets of pistons could be used as long as there is at least one more piston than wall'means or divider 30vfixed to housing 22 and which divides the annular cylinder 32 formed between housing 22 and rotor 24 into two sections. For example, if three wall means are used, there would be four pistons.

The pistons are retractable into the rotor during rotation. Normally the pistons are biased outwardly to be fully extended to sweep chamber 32, as shown by piston 26a in FIG. 1. Retraction is effected by contact with ramp means 34 and 36 which are formed in the opposite sections on the inside of chamber 32 so that rotation of rotor 24 causes the pistons to ride up the ramp means and be retracted into the rotor.

The edge 38 of ramp 34 shown vertically in FIG. 1 is constructed to act as a divider wall as in the case of wall 30. Accordingly, the chamber 32 includes section E (for exhaust) on the inclined side of ramp 34, section 8 (for suction) on the inclined side of ramp 36, section C (for compression) formed by an auxiliary chamber 40 surrounding the outer end of wall 30, and section P (for the power stroke) on the other side of wall 30 from ramp 36. Openings 42 and 44 are formed on either side of wall 30 to connect sections S and P to section C, respectively. Conduits 46 and 48 are connected to chamber 32 on either side of wall edge 38, respectively.

In operation the rotor is rotated in the direction of the arrow in FIG. 1. Conduit 46 is an inlet conduit as indicated by the arrow, and the air entering section S of chamber 32 through this conduit is pushed along by piston 28a and compressed in section C after passing through opening 42. At the upper end of section S piston 28a rides up ramp 36 and is held in retracted position, such as by a conventional locking arrangement, during the continuing rotation.

At this time piston 26a which is locked in retracted position when rotating through the left half of chamber 32 as shown in FIG. 1 now is extended after passing wall 30. A valving arrangement of a conventional nature as known in internal combustion engines allows a certain amount of compressed air to flow through opening or conduit 44 and drive extended piston 26a through section P into section E for exhaust of the air out of conduit 48. Ramps 34 and 36 may be slotted or otherwise formed to allow the passage of air therethrough. The relationship of the positioning of piston 28a to 26a is such that when piston 28a has completed the compression stroke, piston 26a has rotated sufficiently to open up a volume equal to the air volume compressed by the compression stroke. Accordingly, it is seen that the same volume units of air are simultaneously compressed, passed into chamber C and discharged from chamber C into section P.

From FIG. 1 it is seen that pistons 26b and 2811 are retracted while the corresponding two pistons are extended. In practice piston 28b is retracted as it rotates on the right side of chamber 32 in FIG. 1, and it is operable as described above for piston 28a on the left hand side of chamber 32. correspondingly, piston 26b is retracted as it rotates through the left hand side of chamber 32 and operable as described above for piston 26a as it rotates through the right hand side of chamber 32.

It is appreciated that conventional lubrication and ignition would be provided in engine 20. For example, the ignition and injection of fuel could take place in chamber C and the upper part of section P to increase the power output on the piston.

In FIGS. 2 and 3 there is shown a generic embodiment of the improved rotary fluid unit. The stationary housing 50 has a rotor 52 mounted on a shaft 51 and having a flange 54 to rotate on bearings 56. Between the rotor 52 and the housing 50 an annular chamber 58 is formed. A wall 60 fixed on housing 50 divides chamber 58 into two sections within which vanes 62 and 64 rotate. Vanes 62 and 64 are retractable into rotor 52 in order to pass by wall 60 during rotation. Vanes 62 and 64 are normally biased into extended position by springs 66. Cams 70 and links 72 are mounted on the housing 50 and rotor 52, respectively, to cam the vanes 62 and 64 into the retracted position during rotation.

Inlet conduit 74 is located on one side of wall 60, and outlet conduit 76 is located on the other side of wall 60. In operation as a pump rotor 52 is driven so that the suction by vanes passing wall 60 in the direction of the arrow will draw fluid in through conduit 74. The vane following will then force the fluid around chamber 58 and pump it out conduit 76.

FIG. 4 shows the rotary fluid unit in the embodiment of a motor wherein a pump 80 draws fluid from sump 82 and directs it into chamber 84 to drive vanes 86 and 88 and provide a power output from the rotor 90 and its connected shaft (not shown). The fluid is then discharged through conduit 91.

In FIG. the rotary fluid unit is shown embodied in a brake. In this embodiment pump 92 draws fluid from sump 94 to provide pressure fluid through inlet conduit 93 into chamber 96. As in the embodiment of FIGS. 3 and 4 vanes 98 and 100 are driven by the pressure fluid, and the fluid is discharged from conduit 102. Setting of pressure limiting valves 104 and 106 (provided in cross connecting passages 108 and 110), determines the maximum pressure obtainable in chamber 96 for braking purposes. By changing the speed of pump 92 the braking pressure available can be varied. The use of two cross passages 108 and 110 and the valves 104 and 106 allow clockwise or counterclockwise operation in which case pump 92 is rotational in opposite directions.

In FIGS. 6, 7 and 8 another embodiment is shown for movement of the rotating vanes. Inclined track or ramp means 120a and 120b are provided on either side of wall 122, respectively. It will be seen that such track allows an axial displacement of the vanes to pass by the wall 122 rather than a radial retraction as seen in FIGS. 1 and 2. The axial displacement avoids the problem of radial unbalance that could occur in the FIGS. 1 and 2 embodiment although counterweights also could be used. In operation vane 124 rotates in chamber 126. Vane 124 is normally biased to be axially extended by spring 128. During rotation as vane 124 approaches wall 122, it is guided upwardly against spring 128 as it contacts tract 120a. After passing wall 122 vane 124 then is guided down track 1201) to continue sweeping chamber 126. Since the ramp means 120a, 12% are on either side of wall 122, it will be appreciated that operation of the rotary fluid unit in either direction is possible. The construction as illustrated provides radial units that can be very flat, small and powerful, or they can be built larger and more powerful.

FIGS. 9 and disclose the use of a plurality of concentric annular chambers. The chambers 130, 132, 134 and 136 may be of the same cross-sectional area or they may vary in cross-sectional area. However, it will be appreciated that the tot-a1 volume of each chamber varies and the individual power output will vary accordingly as the pairs of vanes 140, 142, 144, 146, 148, 150, 152 and 154 sweep through the respective chambers. Individual walls 160, 162, 164 and 166 separate each chamber, respectively into sections for operation as described hereinbefore with the other embodiments. All chambers and vanes are included in a common housing 168 and mounted on a common shaft 170. Although not shown in the schematic drawing of FIG. 9, it is understood that all vanes would have a common connection to the center rotor 167. However, the outer vanes need only retract sufiiciently to clear their respective walls. It will be appreciated that output of power can be varied by varying the selection of chambers delivering the output to respective conduits (not shown). Another procedure would be to vary the selection of fluid intake conduits to the various chambers.

In FIG. 11 is shown a further embodiment in which the longitudinal dimension of the annular chamber'of the rotary fluid unit is varied to thereby vary the chamber volume and provide an infinitely variable output arrangement. Such variation will vary the torque being transmitted. This follows from the fact that with a constant power input, there will be a constant amount of force being put into the annular chamber. However, if the volume of the chamber is changed, then the result of this force changes, and since torque is the product of force and distance, then the torque is thereby varied. Rotor 176 attached to shaft 178 rotates vane 180 through annular chamber 182 as described hereinbefore. In FIG. 11 the dividing wall in chamber 182 is not shown. Chamber 182 is variable in volume due to the selected position of disc insert 184 which is held in place by plunger 186. A washer member 188 having a dished-in side to receive plunger elements 186 is in abutment with insert 184 which in turn abuts vane 180 that is biased in the opposite direction by spring 190. The other end of plunger elements 186 abuts member 192 which is longitudinally movable along shaft 193 for positioning the vane. The plunger elements are removable to apply additional inserts to change the longitudinal dimension. By adding inserts less volume of chamber 182 is swept by the vane 180 and the torque output is varied accordingly. Adding or decreasing inserts is therefore seen to provide the infinite variation of the torque output. Alternatively the longitudinal movement of member 192 moving plungers 186 would provide the infinite variation of the output in the embodiment of FIG. 11.

To provide self regulating infinitely variable output, member 192 could be so spring or otherwise biased that in the absence of any pressure in chamber 182 the bias on 192 pushes plunger 186 and split washer 188 upward, placing insert 184 very close to rotor 176, and thus reducing chamber 182 to a minimum cross-section.

As fluid enters the chamber 182, pressure builds up, pushing 184, 188, 186 and 192 downward, increasing the cross-section of chamber 182 to the point where the exposed part of vane 180 provides a torque and speed of rotation to shaft 178, which is equal to the power being put into the entering liquid by an external (not shown) power source. Subsequent changes in power delivery from the external source, and/or power demand by the load on shaft 178, will instantaneously reflect themselves in chamber pressure, thus changing both the force per unit area of vane 180, as well as its area exposed to such force.

The bias on 192 can be so designed that to open up the full cross-section of 182 (thus achieving full exposure of 180), the maximum safe chamber pressure needs to develop.

It is understood, that similar self-regulation will be achieved by biasing rotor assembly 198 downward in FIG. 12, and disk 214 to the right in FIG. 13, in the embodiments described hereinbelow.

In FIG. 12 a further embodiment is shown for varying the volume of the annular chamber 194. In this embodiment the shaft 196 and rotor assembly 198 are axially slidable within housing 200 to provide the variation. Wall 202 is located in chamber 194 and biased by spring 204 to follow the movement of rotor assembly 198. In the FIG. 12 cross-sectional view the vane that rotates in chamber 194 is not shown.

In FIG. 13 a still further embodiment is shown for varying the volume of annular chamber 210. Shaft 212 has a disc 214 which may be formed as two half-discs mounted on shaft 212 and the vanes to rotate therewith and able to slide axially therealong by mechanical or hydraulic actuation to provide the desired variation in volume of the chamber. The wall 216 is biased to follow the axial movement of disc 214. The pair of vanes is not shown in FIG. 13, but it is understood that they would be so positioned in chamber 210 as to fill its entire length and they could be retractable into shaft 212. Conduits 219 are provided on one side of disc 214 as an illustration of hydraulic actuation. Pressure fluid can be selectively forced through conduits 219 with chamber 210 to move disc 214 and wall 216 to the right as shown in FIG. 13 to decrease the working volume of chamber 210. Conversely, fluid can be drawn out of chamber 210 through conduits 219 to allow disc 214 and spring biased wall 216 tornove to the left and increase the working volume of chamber 210. Conduits 217 and 218 are similar to either conduit 46 or 48 shown in FIG. 1 to deliver or exhaust the power fluid. .It is understood that there is a set of conduits 217, 218 on either side of wall 216.

A bypass arrangement can be formed in housing 222 as shown at location X in FIG. 13. A cross-sectional view of an embodiment of such bypass is illustrated in FIG. 14, and this bypass provides a change in the application of the power fluid to the vane in conjunction with the movement of disc 214. Bypass conduit 221 is formed with an opening on either side of wall 216 and allows for the inter-change of power fluid in chamber 210 so that there is no power force on the vane. However, conduit 221 can be closed by sliding disc 214 to cover its opening whereby full force can be applied to the vane. It follows that gradual opening or closing of conduit 221 by disc 214 will allow for smooth application or removal of power. Moreover, at a predetermined location of disc 216 so that only part of conduit 221 is closed, then only a small amount of power fl-uid is applied to the vane and idling of the fluid unit or engine will thereby take place. A similar bypass arrangement is possible in FIGS. 11 and 12; whereby such bypass is in communication with the annular chamber on either side of the wall but is selectively closeable by the movable element that changes the size of the chamber. Obviously, such bypass would serve as a load limiting device for the power source when a bias is used to provide self-regulating chamber size as described hereinbefore.

FIG. 15 shows a control system that is operable in conjunction with the embodiment of FIG. 13 in use as an infinitely variable transmission. This system can be assumed to be associated with a motor (not shown) operating at a constant r.p.m. at normal load. In such case speed lever 230 remains upright as shown in full lines in FIG. 15, and governor 232 has a normal rotation as shown. Now if there is an increase in the load, the motor will slow down and the balls of governor 232 will contract moving the lower end of lever 236 to the left as in the dotted line position. Thereupon connected link 244 forces U bracket 246 downward as shown in dotted lines to shift valve 234 so that pressure fluid from pump 238 will enter from conduit 248 into conduit 242. A cylinder 260 has conduit 242 connected at one end, and the pressure fluid forces piston 262 to the right as shown in FIG. 15. Piston rod 264 extends from piston 262 and could be mechanically connected to disc 214 (FIG. 13) to increase the size of chamber 210. Accordingly, it is seen that the control system of FIG. 15 is responsive to a load change to move the disc 214 and thereby provide an automatic variable transmission of the torque output.

It will be understood that the control system is also operable in conjunction with the embodiments of FIGS. 11 and 12 whereby movement of piston rod 264 would automatically effect corresponding movement of memher 192 in FIG. 11 or rotor assembly 198 in FIG. 12.

It will further be understood in connection with the control system of FIG. 15 that a decrease in load will tilt lever 236 in the opposite direction as the motor overspeeds and the balls of governor 232 swing out. U bracket 246 thereupon moves upwardly and pressure fluid is connected from conduit 250 through conduit 240 to the left side of piston 262. The resulting movement of piston rod 262 to the left by a mechanical connection could move disc 214 to the left to decrease the size of chamber 210 so that less torque is delivered as required.

The particular embodiment of the invention illustrated and described is to be considered illustrative only. The present invention includes such other modifications and equivalents as may readily occur to those skilled in the art, within the scope of the appended claims.

What I claim is:

1. A rotary fluid unit comprising a housing having an annular chamber formed therein, wall means radially positioned to divide said chamber into sections, at least two retractable elements connected to a central rotor to rotate within said sections and act upon fluid received therein, a disc element fixed on said rotor and slidable therealong to vary the volume of said chamber to provide an infinite variation of the torque available from the fluid acted upon, and a bypass conduit located within said housing to allow communication between parts of the annular chamber on either side of said wall means to prevent fluid pressure acting on said retractable elements.

2. A rotary fluid unit comprising a housing having an annular chamber formed therein, wall means radially positioned to divide said chamber into sections, at least two retractable elements connected to a central rotor to rotate within said sections and act upon fluid received therein, a disc element fixed on said rotor and slidable therealong to vary the volume of said chamber to provide an infinite variation of the torque available from the fluid acted upon, and a bypass conduit located within said housing to allow communication between parts of the annular chamber on either side of said wall means to prevent fluid pressure acting on said retractable elements, said disc element movable to change the volume of said chamber being adapted to gradually close the bypass conduit to allow a gradual application of fluid pressure to said retractable elements.

3. An infinitely variable transmission system comprising a device responsive to change in a connecting linkage, a rotary fluid unit comprising a housing having an annular chamber formed therein, wall means radially positioned to divide said chamber into sections, at least two retractable elements connected to a central rotor to rotate Within said sections and act upon fluid received therein, a disc element fixed on said rotor and slidable therealong to vary the volume of said'chamber to provide an infinite variation of the torque available from the fluid acted upon, and a bypass conduit located within said housing to allow communication between parts of the annular chamber on either side of said wall means to prevent fluid pressure acting on said retractable elements, a change in the load operating said device and connected linkage effecting movement of said disc element to provide selective infinite variation of torque output from said rotary fluid unit.

4. An infinitely variable pressure transmission system comprising a governor device responsive to change in speed, a linkage connecting said governor device to a valve unit controlling the output of a pump to a cylinder and piston unit, a rotary fluid unit comprising a housing having an annular chamber formed therein, wall means radially positioned to divide said chamber into sections,

at least two retractable elements connected to a central rotor to rotate within said sections and act upon fluid received therein, a disc element fixed on said rotor and slidable therealong to vary the volume of said chamber to provide an infinite variation of the torque available from the fluid acted upon, and a bypass conduit located within said housing to allow communication between parts of the annular chamber on either side of said wall means to prevent fluid pressure acting on said retractable elements, a change in speed of said system operating said device to actuate said valve so that said piston is moved to effect corresponding movement of said disc element and provide selective infinite variation of torque output from said rotary fluid unit.

5. A rotary fluid unit comprising a housing having an annular chamber formed therein, wall means radially positioned to divide said chamber into sections, at least two retractable elements connected to a central rotor to rotate within said sections and act upon fluid received therein, one or more of a plurality of disc insert means being insertable into said chamber to decrease the volume thereof, said retractable elements abutting said disc means and being axially movable by the placement of said insert means against the bias of a spring that presses said retractable elements against said insert means, a plunger means projecting into said chamber and abutting the side of said insert means opposite to the side ab-utted by said retractable elements, and said plunger elements being held 2 in position by an axially slidable element mounted on said central rotor.

DONLEY J.

References Cited UNITED STATES PATENTS Roberts 103-139 Small 91-126 Von Pittler 91-126 Evans 123-16 Durman 103-135 Leiman 103-135 Petersen 103-139 Dooley 103-139 Cady 103-139 Canfield 123-16 Frederick 103-120 Adams et al. 103-120 STOCKING, Primary Examiner.

MARK NEWMAN, WILBUR J. GOODLIN,

Examiners. 

1. A ROTARY FLUID UNIT COMPRISING A HOUSING HAVING AN ANNULAR CHAMBER FORMED THEREIN, WALL MEANS RADIALLY POSITIONED TO DIVIDED SAID CHAMBER INTO SECTIONS, AT LEAST TWO RETRACTABLE ELEMENTS CONNECTED TO A CENTRAL ROTOR TO ROTATE WITHIN SAID SECTIONS AND ACT UPON FLUID RECEIVED THEREIN, A DISC ELEMENT FIXED ON SAID ROTOR AND SLIDABLE THEREALONG TO VARY THE VOLUME OF SAID CHAMBER TO PROVIDE AN INFINITE VARIATION OF THE TORQUE AVAILABLE FROM THE FLUID ACTED UPON, AND A BYPASS CONDUIT LOCATED WITHIN SAID HOUSING TO ALLOW COMMUNICATION BETWEEN PARTS OF THE ANNULAR CHAMBER ON EITHER SIDE OF SAID WALL MEANS TO PREVENT FLUID PRESSURE ACTING ON SAID RETRACTABLE ELEMENTS. 